Hydraulic coupling



Nav. 1o, 1942. H. SUQCLMR 2,301,645

HYDRAULI C C OUPL ING Filed April 2, 1941 4 sheets-sheet 2 Patented Nov. 1o, 1942 HYDRAULIC OOUPLING Harold Sinclair, Kensington, London, England Application April 2, 1941, Serial No. 386,391 In Great Britain April 17, 1940 1,3 Claims.

This invention relates to hydraulic couplings of the kinetic type. It is especially, but not exclusively, concerned with 'such couplings which are intended to operate at all times with a substantial quantity. of working liquid in the working circuit, and preferably with a reservoir space having a capacity which is relatively small compared with that of the working circuit, the arrangement being such that liquid is transferred between the reservoir space and the working circuit automatically in accordance with variations in the operating conditions. The reservoir space, when provided, is preferably included within the rotary parts of the coupling, although it may be provided by a stationary chamber connected to the coupling by a duct.

In many applications of such hydraulic couplings, such as for traction purposes with internal-combustion engines or electric motors, and on cranes, excavators and like machinery, and in stationary plant for internal-combustion and electric motor drives, certainconilicting characteristics are desirable.

The first desirable characteristic quality is that the slip shall be low, and the power transmission efllciency consequently high, at normal running speeds even under high torques.

Secondly, that the drag torque shall be low, that is the torque transmission capacity when the runner` is stalled. For example, in the case of a vehicle drive, it is desirable that the drag v torque should be low when the internal-combustion engine is idling with the gear engaged, so that there lis only a small creeping tendency.

Similarly, if the coupling is used to facilitate the starting o f a squirrel-cage electric motor when connected by the coupling to a load requiring a high starting torque, it is necessary that the stalled torque ofthe couplingshould not ordi- ,narily exceed about twice the rated full-load torque at a motor speed of the order of 90% of synchronous speed.

Thirdly, it is very important that once the runner has begun to rotate when being acceler- 'ated from rest against the load, the slip shall ity of the coupling should not attain an excessively high value, as compared with the normal full-load torque,v when both the impeller speed and the slip are high, in other words the coupling shall have satisfactory torque-limiting qualities.

Themain object of this invetn'ion is to provide a hydraulic coupling which has, in combination;-

in particular thefirst three of the above-mentioned desirable though conflicting characterisl tics, and which nevertheless is low in production cost, and is simple, compact and reliable, being adapted to operate automatically and not requiring the complication of control mechanism, such as a centrifugal governorl or a slidable hydraulic element.

According to this invention a hydraulic coupling of the kinetic type includes an annular workingcircuit which is formed by the impeller and runner elements and in which the working liquid can circulate in the form of a vortex ring, this circuit being :free from annular members in its interior, shaped to guide the circulation of the liquid, and the said elements each having a number of varies not less than isgiven by either of the formulas: N=14.67D2", where D is the outer prole diameter of the working circuit in inches and ranges from 9 inches upwards (or N=11.4D2", where D ls in centimetres and ranges from 23 cm. upwards), and N=8+2D where D is in inches and ranges from 9 inches downwards (or N=8+0.79D where D is in centimetres and ranges from 23 cm. downwards), the coupling also including a deilector on the boundary of the working circuit adapted to interrupt the flow of `the vortex ring of liquid in the neighbourhood of its boundary. For practical reasons concerned with'manufacture, the number of vanes it is lconvenient to provide in the elements of a hydraulic coupling decreases with reduction in the size of coupling, and in order to promote smoothness of running it is customary to arrange for a small dilerence in the numbers of vanes in the impeller and the runner respectively.

Fig. 1 of the accompanying drawings shows numbers of vanes as abscissa to size of coupling ber of vanes in the improved couplings, and curve D vgives the preferred minimum number of vanes indicate the recommended numbers of vanes on the impeller and runner when these elements are castings. The number of vanes on each element is conveniently arranged to be a multiple of three, and t'o prevent encroachment on the liquid passages near the axis of rotation, two out of every three adjacent vanes are cut away here, so that two short vanes alternate with one long vane. One vaned element conveniently has three-more vanes than the other, and these recommended numbers of vanes lie within a range of between 1 and 9 more than the value given by curve D. The recommended numbers of vanes accordingly lie `within either of the ranges N=10+3D to N=18I3D Where D is in inches and does not exceed 9, and N=1-}19.4D29 to N=9+194D029 where D exceeds 9 inches. The maximum num- ,ber of vanes that can be usefully provided is determined by practical questions of manufacture and cost.

The invention will be further described with reference to Figs. 2 to 9 of the accompanying drawings, in which- Fig. 2 is a sectional side elevation of part of one type of the improved coupling, Q

Fig. 3 shows speed/ time curves of they improved couplings taken under acceleration conditions,

Fig. 4 shows corresponding curves of lmown couplings, Fig. 5 shows the relationship of torque-transmission capacity to slip of the improved couplings. v

Figs. 6 to 8 compare the torque/speed and slip/speed characteristics of the improved couplings and of known standard couplings, and

Fig. 9 is a sectional side elevation 'of part of another type of the improved coupling.

In the example shown in Fig. 2 the impeller I0 is mounted on a driving shaft II in known manner by means of a part-spherical spigot I2 and a ilexible diaphragm I3. The runner I4 is juxtaposed to the impeller I to form therewith an vannular working circuit having a smoothly curved profile. In the example shown the outer profile diameter DI is 12.75 inches (32.4 cm.) and the inner profile diameter D2 is 3.95 inches (10 cm.) The impeller I0 has forty-eight vanes alternately one long vane I and two short vanes I6, and the runner has forty-five vanes alternately one long vane I'I and two short vanes I8. A rotary casing I9, provided with a lling plug 20, is xed by bolts 2| to the -periphery of the impeller II'I and covers the back of the runner I 4. The radially outer part of the casing I9 lies close to the back of the runner, while the radially inner part of the casing is spaced from the back of the runner groove ball-bearingl 28 is supported in a housing 29 in the hub of the casing I9 and supports the other end of the shaft 26. Oneach side of the a beading which Abears resiliently on the adjacent side of the inner race of the bearing 28, which is clampedon the shaft 26 by a nut 33. The diaphragms co-operate with the bearing to form a gland which prevents leakage of oil from the coupling and ingress of dirt to the bearing.

The deector in the working circuit consists of a flat annular baille 34 xed between the runner and the flange 25 and projecting into the working circuit at the radially innermost part of the circuit. 'I'he size of this baiiie is conveniently described in proportion to the inner profile diameter. The baille shown is a 1.5 baille, its eX- ternal diameter D3 being 1.5 times the inner prole diameter, namely 5.93 inches (15 cm.). The baille size, with a circuit having the proportions shown in Fig. 2, in whichthe ratio DI /D2 is substantially 3.2/1, may range from 1.3 to 1.8, and particularly favourable results are obtained with a size of 1.5 or 1.6. Expressed in another way, the baille may project into the working circuit to a. distance ranging from 131/2 to 36 per cent of the difference between the inner and outer profile radii, the particularly favourable results being obtained when the figure is 221/2 to 27 per cent.

This example has a greatly improved slip characteristic in the full-torque acceleration range,

previouslyreferred to, as compared with known i drag torque, the slip is undesirably high for a substantial way up the acceleration range, even although the slip at higher running speed is satisfactorily low.

A further important advantage of the new coupling is its improved performance with an abnormally small liquid content, as compared with known couplings having the same outer prole diameter which enables the expansion of the working liquid and contained air as the cou.-

to' provide a reservoir space 22 having a capacity of. between one-quarter and one-eighth and preferably aboutone-fth of that of the working circuit, which communicates with the reservoir space through the gap 23 between the peripheries of the impeller and the runner. The runner is xed.by bolts 24 to a. flange 25 on a runner shaft 26 which is journalled at one end by a roller pling temperature rises in use .to be accommodated without the need for an excessively large expansion space outside the working circuit. In consequence the coupling can be relatively short and light. l

Fig. 3 shows the results of test carried out with the couplingshown in Fig12. In these tests the coupling was employed to couple a petrol engine, yielding a torqueof between and 100 lb.ft. (12.5 and 14 kg.m.) to a heavy ywheel provided with a disengageable brake. The brake was applied to hold the flywheel stationary and the engine was run at full torque, the slip in the coupling being 100 per cent. The brake was then released, and, as the ywheel accelerated, the speeds' of the engine 'and of the flywheel were bearing 21`in the hub of the impeller I0. A deep- 75 electrically recorded atl intervalsA of one-*tenth drag torque.

second. These speeds are plotted as ordinates on a time base of seconds. f

' Curves Il and RI show respectively the engine (impeller) speed and the ywheel (runner) speed when the coupling was provided with a 1.4 size badie. The quantity of liquid in the coupling was what is termed a l9degree iilling. That is to say. the maximum that could be inserted when the axis of rotation was horizontal and the impeller was so placed that the hole for the filling plug 20 lay'on a radius inclined at 19 deg. to the vertical. These curves show that the drag torque was reasonably low, since the engine speed when the coupling was stalled was as high as 740 R. P. M. Furthermore as the flywheel accelerated, theslip dropped to a very low value before the engine speed exceeded 1000 R. P. M.

Curves I2 and R2 of Fig. 3, which relate to the same coupling with the 1.4 size baiile but with a 50-degree filling (i. e., such that only about three-quarters of the total internal space of the coupling contained liquid) show particularly valuable characteristics. The engine speed at full torque with the ilywheel brakedwas as high as 1000 R. P. M. indicating a very low On release of the flywheel brake the rise in torque transmission capacity was so rapid that the engine speed at full throttle was pulled down 4to a minimum of 890 R. P. M., and when the engine had again accelerated to 1000 R. P. M., 13 seconds after the flywheel had started, the slip was only l5 per cent., and after 22 seconds at 1500 R. P. M. of the engine at full throttle the slip had dropped to the verylow ligure of 2.67 per cent.

Curves I3 and R3 of Fig. 3 show the results oi' a test of the same coupling fitted with a 1.6 size baille and having a l9-degree filling. In this test the engine speed at full torque with 100 per cent. slip was 870 R. P. M., as compared with 740 R. P. M., `with the 1.4 size baille, while after the runner'speed had attained 800 R. P. M.,

the slip was not appreciably higher than with and curves I6 and R6 relate to the same coupling but with a 5G-degree illling. Even in the Latter test the speed of the engine at full torque and 100 per cent slip was only 840 R. P. M. which indicates arelatively high idling drag torque; and moreover in both tests and particularly in the latter the slip over the acceleration range was excessive up to- 1250 R. P. M. of the runner.

Curves Il and Rl relate to this coupling with a f1.4 size baille? and a 1Q-degree lling, while curves I8 and R8 relate to the same coupling with a 5U-degree illling. While in these two tests the presence of the baille had raised the engine speedfat full throttlerand 100 per cent. slip to satisfactory figures, it was at the expense of a high slip in the latter part of the acceleration range as may be seen by comparing with the ,slips recorded in Fig. 3.

Fig. 5 gives the torque transmission factor K poses of comparison of different couplings) of the curve Kl rises from zero to a peak values at a slip of about per cent. and then falls quite markedly to the stalling point, this humped s'hape being a desirable feature. The curve K2 in the region between 20 per cent. and lminimum slip is practically identical with the curve KI, and furthermore the torque transmission factor is maintained at a substantially uniformly high value in the range between 100 and. 20 per cent. slip, which is an important and valuable feature of the improved coupling. Curves K3 and KI of Fig. 5 relate to the same coupling with a 30- degree filling. characteristic fea-tures as the curves KI and starting the test with the coupling cold, and by the time the slip had risen to 100 per cent. the

coupling temperature had vrisen substantially. The curves K2 and K4 were obtained by starting the tests with the coupling hot. The slight differences in the K values of the two curves for each degree of iilling at 100 per` cent. slip are due to differences of' temperature of the cou- `decreasing impeller speed. 'Curves T2 and T3 i show the drag torques of the improved coupling with 30-degree and 5D-degree llings respectively, and the corresponding slip curves are S3 and S4, which were obtained, unlike the curves SI and S2, under acceleration conditions, which Y are more exacting in the demands on the cou-'- pling. The improved coupling shows a reduction-in drag torque of about one-third. and a reduction in slip of more than one-half, as cornpared with the known coupling.

Fig. 7 is a comparison, similar to Fig. 6, between another known standard hydraulic coupling and the improved coupling, both having an (a non-dimensional quantity employed for purouter profile diameter of 14 inches (35.6 cm),

the engine torque being 210 1b.f.t. Curves T5 and S5relate to the known coupling, curves T6 and S5 to the improved coupling with the 30- degree filling and curves T1 and S1 to the improved coupling with 5G-degree lling. Slip curves S6 and S1 were also obtained under the more exacting acceleration conditions. In this case the improvements according to the invention have reduced the drag torque by about one- 'third andy the slip by about two-thirds on 'a coupling of the same outer prole diameter.

They have the same desirable The curves KI and'K3 were obtained by Fig. 8 similarly compares yet another known standard hydraulic coupling having an outer prole diameter of 16 inches (40.5 c. m.) with the improved coupling of the same size, under an engine torque of 260 lb.ft. Curves T8 and S8 relate to the known coupling; curves S9, SII! and SII relate to the improved 'coupling with ings, and curve TII) is the dragtorque curve of the improved coupling with a 3U-degree" filling. The improved coupling halves the drag torque and also reduces the average slip by one-half.

A remarkable feature of the slip curves of the improved couplings in Figs. 6, 7 and 8 is the drop,

on acceleration, from 100 per cent. slip to a value as low as 20 per cent. with 5D-degree lling before the engine speed begins to exceed the value it had when the slip was 100 per cent.. and thereafter a reasonably rapid reduction in slip to a very low value. This feature yields a substantial economy in fuel consumption of veimproved characteristicsare maintained with reduction in drag torque, though the slip is slightly increased as the baie size approaches the 1.8 value.

Another example of the improved coupling, made largely of steel pressings welded together, is shown in Fig. 9. This coupling has the same profile diameters and the same numbers of impeller and runner vanes as the coupling shown in Fig. 2. The runner I4A is proportioned simiwith a baiile. The runner vanes IIA and I8A are provided with integral lugs 40 which are spot welded tothe pressed steel shell of the runner, and they are braced together by means of a stiffening ring 48 to which they are welded. The section of the ring 48 is so small that it has no appreciable guiding effect on the vortex ow. The hub of the runner shell is reinforced by a pressed steel ring 4I and spot welded to a ange A on the runner shaft 2 6A. The impeller IDA has a hub of relatively increased diameter so arranged that its end face 34A forms the deflector fordiverting the outer layer of the liquid vortex radially outwards as it leaves the runner. The

circuit boundary of the impelller curves gradualto a flanged hub 29A which projects into the middle of the reservoir space 22A andv formsa housing for a runner-shaft bearing 28A and diaphragm glands disposed somewhat similarly to the corresponding parts in Fig. 2'. This arrangement secures a substantial reduction in the length of the coupling, as compared with the standard f culate in the form of `a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and the said elements each having a number of vanes not less than is given bythe formulas: N =8+2D where D does not exceed 9, and N=14.6'7D027 where D exceeds 9, N denoting the number of vanes and D the outer profile diameter of the '40 larly to that'shown in Fig. 2, but is not provided v ly outwards from .the outer edge of the face 34A.

Apertures such as 49 are formed in the ring 4I and in the hub of the runner shell so as to put the v space 5I within the hubof the impeller shell into communication with the reservoir space 22A provided between the rotary casing ISA and the runner shell.

The impeller vanes ISA and IIBA have lugs 4I)` welded to the impeller shell which is spot'welded to a anged boss 42 to which.. the driving shaft IIA is secured. The vanes ISAand I6Aare braced together by means of astiiening ring 50 to which they are welded and which, likethe ring 48, has a section so small that it has no appreciable guiding effect on the vortex ow. The inner edge of the impeller shell is secured to the boss 42 by a continuous welded seam 43.

The rotary casing I 9A, which is welded at 44 to the impeller shell, is also welded at'46` land 41 75 working circuit in inches, the coupling also including a deiiector on the boundary of the working circuit positioned to interrupt the iiow of the vortex ring of liquid in the neighbourhoodKiof its boundary.

2. A hydraulic coupling of the kinetic type including an annular working circuit which is formed by an impeller element and a runner element and in which the working liquid can circulate in the form of a vortex ringQths circuit being free from annular members in its interior I shaped to guide the circulation of liquid, and the said elements each having a number of vanes not where D exceeds 9, N denoting the number of vanes and D the outer profile diameter of the working circuit in inches, the coupling also including a deector on the boundary of the working circuit positioned to interrupt the ilow of the vortex ring of liquid in the neighbourhood of its boundary.

3. A hydraulic coupling of the kinetic type including an annular working circuit which is formed by an impeller element and a runner element and in which the working liquid can circulate in the form of a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and the said elements each having a number of vanes lying within the ranges N=10+3D and N=18+3D, where D does not exceed 9, and 1 \I=1}19.4D02g and N=9+19.4D029 where D exceeds 9, N denoting the number of vanes and D the outer prole diameter of the working circuit in inches, the coupling also including a deflector on the boundary of the working circuit positioned to interrupt the ow of the vortex ring of liquid in the neighbourhood of its boundary.

4. A hydraulic coupling of the kinetic type including an annular working circuit which is formed by an impeller element and a runner element and in which the working liquid can circulate in the form of a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and the said elements eachhaving a number of vanes lying where D does not exceed 9, and N=1i19.4D029 and N=9+19iDll29 where D exceeds 9, N denotmg the number of vanes and D the outer pronle diameter of 'the working circuit in inches, the

varies on each of said elements numbering a multiple of three and consisting of one long vane alternating with two short vanes, the coupling also including a deector on the boundary of the working circuit positioned to interrupt the flow of the vortex ring of liquid in the neighbourhood of its boundary.

5. A hydraulic coupling of the kinetic type including an annular working circuit which is formed by an impeller element and a runner clement and in which the working liquid can circulate in the form of a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and the said element-s each having a number of vanes not less than is given by the formula: N=9+3D where D does not exceed 9, and N=19.4D29 where D exceeds-9, the number of vanes on each of said elementsbeing a multiple of threeV and the number of vanes on one of said elements exceeding the number of vanes on the other of said elements by three, the coupling also including a defiector on the boundary of the working circuit positioned to interrupt the flow of the vortex ring of liquid in the neighbourhood of its boundary.

6. A hydraulic coupling oi' the kinetic type including an annular working circuit which is formed by an impeller element and a runner element and in which the working liquid can circulate in the form of a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and the said elements each having a number of varies not less than is given by the formulas: N=8+2D where D does not exceed 9, and N=14.67D2' where D exceeds 9, N denoting the numberof varies and D the outer prole diameter of the working circuit in inches, the coupling also including a deilector on the boundary of the working circuit positioned to interrupt the ow of the vortex ring of liquid in the neighbourhood of its boundary, said deflectr being disposed on the part of the boundary of the working circuit nearest to the axis of rotation of the coupling and having an external diameter exceeding 1.4 times the inner profile diameter of the working circuit, the .ratio of the outer to the inner profile diameter being substantially 3.2/1.

'7. A hydraulic coupling of the kinetic type including an annular working circuit which is formed by an impeller element and a runner element and in whi-ch the working liquid can circulate in the form of a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and

where D exceeds 9, N denoting the number of vanes and D the outer profile diameter of.l the `Working circuit in inches, the coupling also including a deflector on the boundary of the workingcircuit positioned to interrupt the flow oi the vortex ring of liquid in the neighbourhood of its boundary, said deiiector being disposed on the part of the boundary of the working circuit nearest to` the axis of rotation of the coupling and projecting into the working circuit to a distance exceeding 17.5 per cent. of the diierence between the inner and outer profile radii of the working circuit.

9. A hydraulic coupling of` the kinetic type including an annular Working circuit which is .formed by an impeller element and a runner element and in which the working liquid can circulate in theform of a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and the said elements each having a number of varies not less than is given by the formulas: N =8+2D where D does not exceed 9, and N=14.67DU27 where D exceeds 9, N denoting the number of varies and D the outer prole diameter of the working circuit in inches, the coupling also 1ncluding a deflector on the boundary of the working circuit positioned to interrupt the flow of the vortex 'ring of liquid in the neighbourhood of Iits boundary, said deflector being disposed on the part of the boundary of the working circuit nearest to the axis of rotation of the coupling and projecting into the working circuit to a distance l ranging between 221/2 and 27 per cent. of the dii'- the said elements each having a numbenof vanes not less than is given by the formulas: N=8+2D where D does not exceed 9, and N=14.6'7D01"rl vwhere D exceeds 9, N denoting the number ol' vanes and D t-he outer prole diameter of the working circuit in inches, the coupling also including a deilector on the boundary of the working circuit positioned to interrupt the flow of the vortex ring of liquid in theV neighbourhood oi' its boundary, said deect-or being disposed on the `part of the boundary of the working circuit nearest to the axis of rotation of the coupling and having an external diameter of between 1.5 and 1.6 times the inner prole diameter of the working circuit, the ratio of the outer to t-he inner .protlle diameter being substantially 3,2/1.

8. A hydraulic couplingof the kinetic type formed by an impeller element and a runner including an annular working circuit which is,

ference between the inner and outer Aproie radii of the working circuit.

. 10. A hydraulic coupling of the kinetic type including an annular working circuit which is formed by an impeller elementl and a runner element and in which the working liquid can circulate in the form of a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and the said elements each having a number of vanes not less than is given by the formulas: N=8+2D where D does not exceed 9, and N=14.67D"27 where D exceeds 9N denoting the number of varies and D the outer profile diameter of the working circuit in inches, the coupling also including a deflector on the boundary of the working circuit positioned to interrupt the flow of the Vortex ring of liquid in the neighbourhood of its boundary and a rotary casing attached to the periphery of one of said elements and spaced from the back of the other of said elements to form a reservoir space having a capacity of between one-quarter and one-eighth of the volume of the working circuit.

11. A hydraulic coupling of the kinetic type including an annular Working circuit which is where p does not exceed 9, and 1v=14712-27 where D exceeds 9,'N denoting the number of varies and D the Qouter profile diameter of the Working circuit in inches, said impeller having a hub the diameter of which exceeds the inner prole diameter of the runner and an end face` said elements each having a number of vanes not less than is given by the formulas: N=8+2D where D does not exceed 9, and N=14.67D-2" where D exceeds 9, N denoting the number of vanes and D the outer profile diameter of the working circuit in inches, the said impeller havking a hub the diameter of which exceeds the inner prole diameter of the working circuit and an end face of which forms a deiiector projecting into the working circuit to a distance exceeding 17.5 per cent. of the difference between the inne and outer prole radii of the runner.

13. A hydraulic coupling of the kinetic type including an impelier clement and a runner element together forming a working circuit in which the working liquid can circulate in the form of a vortex ring, this circuit being free from annular members in its interior shaped to guide the circulation of liquid, and the said elements each having a number of vanes not less than is given by the formulas: N=8|2D where D does not exceed 9, and N=14.6'1D2" where D exceeds 9, N denoting the number of varies and D the outer proiile diameter of the working circuit in inches, the coupling also including a deiiector or the boundary of the working circuit position to interruptv the ow of the vortex ring of liquid in the neighborhood oiits boundary, said deflector being disposed lon the part'of the boundary of the working circuit nearest to the axis of rotation of the coupling and projecting radially outwards of the inner profile radius of said runner to a distancenot less than 17 1A.; per cent. of the` difference between said radius and the outer prole radius of said working circuit, and a rotary casing attached to the periphery of one of said elements and spaced from the back ofA the other of said elements to form a reservoir space having a capacity of between one-quarter and one-eighth of thevolume of said working circuit.

HAROLD SINCLAIR. 

